CN108138877B - Wear optimized blade design - Google Patents
Wear optimized blade design Download PDFInfo
- Publication number
- CN108138877B CN108138877B CN201680055433.4A CN201680055433A CN108138877B CN 108138877 B CN108138877 B CN 108138877B CN 201680055433 A CN201680055433 A CN 201680055433A CN 108138877 B CN108138877 B CN 108138877B
- Authority
- CN
- China
- Prior art keywords
- brake pad
- brake
- pad
- disc
- carrier mount
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
- F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
- F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
- F16D65/095—Pivots or supporting members therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D2065/026—Braking members; Mounting thereof characterised by a particular outline shape of the braking member, e.g. footprint of friction lining
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Braking Arrangements (AREA)
Abstract
A brake pad for a disc brake having reduced wear characteristics is provided. The brake pad is configured such that a distribution of brake pad friction material is weighted toward a radially outer region of the brake pad, with lateral sides of the pad material generally aligned with a radial line having an origin at an axis of rotation of a brake rotor of the disc brake. The brake pad friction material distribution results in a reduction in brake application pressure between the brake pad and the brake disc while achieving the same braking force provided by a comparable generally rectangular brake pad, which results in less brake pad wear and the same level of braking force.
Description
Cross Reference to Related Applications
This application claims the benefit of U.S. application No.14/844, 813, filed on 3/9/2015, the contents of which are incorporated herein by reference in their entirety.
Technical Field
The present invention relates to a disc brake for a vehicle, and in particular to a brake pad in a disc brake such as an air-operated disc brake utilized on commercial vehicles.
Background
Fig. 1 shows an example of a commercial vehicle air-operated disc brake. In the embodiment of fig. 1, the disc brake 1 comprises a brake disc 2, the brake disc 2 rotating in a direction a about its axis of rotation B. The brake caliper 3, which spans the brake disc 2, is secured to a carrier mount 4, which carrier mount 4 is in turn secured to the axle, typically by a torque plate or brake bracket (not shown). In the present embodiment, the carrier mount 4 receives and supports the caliper 3 and the brake pads 6. In this embodiment, the jaws 3 are actuated by pneumatic actuators (not shown) mounted on the actuator mounting faces 5 of the jaws. The actuator acts on a brake pad application mechanism contained within caliper 3 to press brake pads 6 against brake disc 2, thereby slowing the vehicle. The invention is not limited to a particular type of brake actuator, for example, a pneumatic actuator or an electric actuator may be used. The invention is also not limited to a particular type of caliper mount arrangement. For example, the brake caliper may be mounted in a manner fixed to the carrier, or may be a sliding caliper.
In disc brake applications, such as commercial vehicle disc brakes, the brake pads typically have a generally rectangular shape, in part because of limitations on the size and configuration of the disc brake assembly (the disc brake must reside within a housing that is limited in the height of the space provided by the wheel rim), in part because of cost and structural limitations discussed further below. Fig. 4 shows an example of such a previous brake pad.
A common feature of the previous brake pads 20 is that they have substantially parallel side faces 22,23, etc., the pad sides facing the circumferential direction of the brake disc towards the adjacent pad abutment surfaces being parallel to each other. The generally rectangular shape may include the radially inner and radially outer sides of the brake pads 24, 25 that are slightly curved to generally follow the curvature of the brake disc, as shown in FIG. 4, or in the case of the radially outer side, follow the shape of the adjacent outer regions of the caliper. (not shown). The use of parallel side surfaces of brake pads has been the de facto standard in commercial vehicle disc brakes to some extent, partly because of practical manufacturing considerations (e.g., lower cost brake pad abutment surfaces and machining of parallel side brake pad backing plates), and partly because of structural reasons to ensure adequate brake pad abutment strength, wear and brake force absorption performance.
Due to their generally rectangular shape, previous commercial vehicle disc brake pads have exhibited brake discs having substantially constant width and height profiles from one side of the brake pad to the other. This brake pad shape has several disadvantages during the braking operation. Among these disadvantages is that the specific braking energy transfer from the brake disc to the brake pad is not constant across the radial height of the brake pad. Instead, this energy transfer varies as a function of radial height relative to the axis of rotation of the brake disc (i.e., the braking torque varies as a function of distance from the axis of rotation of the brake disc, where force x distance is torque) and varies as a function of the length of the friction surface of the pad friction material at different radial heights. As a result, energy transfer to the brake pad and resulting localized wear of the brake pad is inconsistent across the face of the brake pad friction material. This may lead to premature wear of the friction material in some areas of the brake pads and thereby shorten the time before the brake pads must be replaced.
Disclosure of Invention
The present invention addresses this and other problems by providing a brake pad having a more efficient and uniform distribution of braking energy delivery across the face of the pad lining material. The method of the present invention provides more uniform pad lining material wear, thereby extending the service life of the brake pad. Improved brake pad performance also enables the overall brake size to be reduced by allowing smaller brake pads to be used, while still providing good braking performance.
In an embodiment of the invention, the brake pad lining material, and preferably the brake pad backing plate carrying the lining material, has a generally circular arc shaped profile with a radially outer portion of the lining material having a width in a circumferential direction that is longer than a width of the lining material at a radially inner portion of the brake pad. Preferably, the width of the pad lining material as a function of radial distance from the rotor axis of rotation is established by substantially aligning the sides of the lining material along radial lines intersecting at or near the rotor axis of rotation. The side faces of the brake pads need not be accurately aligned with the radial lines from the axis of rotation; rather, the present invention contemplates the liner material being the largest in width at the radially outer region of the brake pad, while being smaller in width at the radially inner region of the liner material. The closer the intersection point is to the center of the brake disc rotor, the more efficient the energy distribution at the disc interface.
Another further advantage of the present invention is that the reduced width in the radially inner region of the brake pad allows the abutment surfaces of the brake pad carrier and the side surfaces of the brake pad to meet a line along a radius more approximately perpendicular to the secondary axis of rotation. This arrangement allows the braking force to be transmitted between the lateral surfaces of the brake pad and the pad abutment surfaces of the pad carrier perpendicular or nearly perpendicular to the abutment line. This distributes the abutment force more evenly over the abutment surface, i.e. a more even (and thus lower) contact pressure, helps to minimize brake pad vibration and associated brake noise, improves fatigue life performance and reduces component wear.
In addition, this arrangement may help reduce the effects of "pad kick", which is a type of in-situ rotation of the brake pad that may produce unwanted brake application noise due to pad vibration, increase fatigue damage to typical brake pad retaining hardware (e.g., leaf springs across the pad), and increase wear and damage to the brake pad and/or brake caliper mounting structure. An illustration of the sheet kickback is provided in fig. 4. When brake pad 101 is applied against a friction surface of a brake disc (not shown) rotating in direction DR, rotation of the brake disc causes movement and reaction forces between brake pad 101 and its adjacent mount abutment surface (not shown). At the leading edge 102 of the brake pad, the pad attempts to move upward in direction LU (illustrated here by force arrows across the face of the pad 101) in response to frictional forces along the face of the pad. At the trailing edge 103 of the brake pad, the brake pad attempts to move downward in direction TD. However, because brake pad 101 is restrained by the adjacent mount abutment surfaces, the overall movement of the brake pad is generally a rotation about an axis parallel to the rotor axis of rotation. This motion may be unidirectional during brake application or may manifest itself as moderate to severe oscillations of the brake pad in its mount, thereby significantly increasing wear against the brake pad and mount surfaces.
Those skilled in the art will recognize that brake pad support functionality may be provided by brake caliper mounts designed to support brake pads, or by brake pad carriers separate from the caliper mounting structure. For ease of description, the terms caliper carrier, caliper mount, and brake pad carrier may be interchanged without intending to limit the brake pad support structure to any particular brake pad and brake caliper carrying structure.
A further advantage of the present invention is that the reduced width in the radially inner region of the brake pad allows the brake pad retaining features, such as disclosed in pending application serial No.14/640,152, to be moved closer together to enable further reduction in the size of the disc brake assembly while maintaining a desired level of braking performance and/or increasing braking performance by increasing the brake pad lining surface area while still maintaining the overall brake size within the spatially limited enclosure of the rim and other nearby components.
Drawings
Other objects, advantages and novel features of the invention will become apparent from the following detailed description when considered in conjunction with the drawings.
Fig. 1 is an oblique view of a disc brake pad.
FIG. 2 is an oblique view of a brake pad according to an embodiment of the present invention.
Fig. 3 is a front view of the brake pad of fig. 2.
Fig. 4 is a front view of a known generally rectangular brake pad, annotated to illustrate pad motion in response to brake application.
Fig. 5 is a front view of an embodiment of a carrier mount configured to supplement the brake pad of fig. 2.
Detailed Description
Fig. 2 is an oblique view of an embodiment of the invention wherein the brake pad 10 includes a backing plate 11 having brake pad friction material 19 adhered thereto. As shown in fig. 3, the side surfaces 12,13 of the brake pad 10 are generally aligned along a radius extending from the axis of rotation (not shown) of the brake rotor 2. The radially inner side 14 and the radially outer side 15 of the brake pad 10 generally follow the curvature of the brake rotor with a slight curvature.
The brake pad backing plate in this embodiment includes lateral projections 16, the lateral projections 16 being formed to engage corresponding brake pad retaining features in the carrier mount 4 in the manner disclosed in co-pending application serial No.14/640,152 such that the brake pad is positively retained within the disc brake once engaged in the receiving features of the carrier mount, even in the absence of any other brake disc retaining means. The backing plate 20 in this embodiment also includes radially outer features including a hook portion 17 adapted to receive brake pad vibration suppression and/or an end of a reaction device (not shown) such as a leaf spring and a notch 18 configured to receive a brake wear sensor (not shown). The brake pad backing plate lateral projections, hook portions and wear sensor notches are features of this embodiment, but are not required by the present invention.
The performance of the invention in terms of braking energy, brake application pressure and reduced brake pad material wear is illustrated by means of figure 3 and the following formula.
Fig. 3 is a schematic annotated front view of the embodiment of fig. 2 of the brake pad of the present invention. As shown in the figure, the angle spanned by the arc of the sheet material 30 with the rotation axis O as the center is the brake disc
The inner and outer diameters of the sheet material are r1And r2. Pressure P used in the following integral calculation1(P2) The incremental area applied thereto is dAB1(dAB2)。
Using this nomenclature, the energy transfer from the brake disc to the brake pad in each incremental area dA is stated as:
wherein
And is
The specific energy at any radius r is
The incremental area is:
dAS(r)＝2πrdr [3]
and thus the specific energy transfer is
Where K is a constant.
Brake pad material wear rate and pressure applied between the brake disc and pad material are known to have a 1: relationship of 1:
Δh＝KPvt [5]
where h is the sheet wear, P is the applied pressure, k is the wear coefficient (depending on the material), and v is the velocity. The pressure and wear therefore have a direct relationship.
The pressure distribution function (and hence sheet material wear) can be obtained from a specific energy transfer formula:
this relationship allows the relative change in wear performance between the two brake pad shapes to be evaluated. Keeping the other variables constant, the pressure (and wear) ratio between the two sheet shapes is:
in the case of brake pads according to the present invention, when both brake pads are applied to generate the same amount of braking force as compared to a generally rectangular brake pad having the same inner and outer diameter heights, the present invention results in a greater brake pad arc length at the radially outer region of the brake pad resulting in greater braking force at a lower local pressure than a generally rectangular brake pad while reducing the amount of braking force required from the pad material at the radially inner region of the brake pad.
For example, in a comparison of a conventional generally rectangular brake pad with one of the inventive brake pad shapes, the inventive brake pad has a greater arc length (the arc angle) of 20cm at the radially outer region of the brake pad
Approximately five degrees, e.g. TongThe radius of the brake rotor and the original arc length of the existing rectangular brake pad). Although the overall pad surface area of the "wedge" pad of the present invention is reduced by 4%, the redistribution of brake application pressure and braking force due to the change in the radial height distribution of the pad material along the pad results in a reduction in the P1/P2 brake application pressure ratio, while still achieving a 1.31: 1, the same braking force. In other words, despite the brake pad material area reduction, with the brake pad arrangement of the present invention, the wear rate is reduced by 31% over existing generally rectangular brake pads.
Fig. 5 is an elevation view of a preferred carrier mount 26 configured to complement the brake pad of fig. 2, having a carrier mount brake pad abutment surface 27 configured to support brake pad 10 in a circumferential direction in response to a brake reaction force generated between the brake pad and the brake pad. This is a preferred embodiment, however, it is not necessary to modify the carrier to obtain many of the benefits of the invention. Since the side surfaces 12,13 of the brake pad 10 (and thus the pad abutment surfaces 27) are generally aligned along a radius extending from the rotor axis of rotation, the transfer of braking forces between the trailing edge of the brake pad 10 and the carrier mount 26 occurs substantially parallel to the tangential direction of rotor rotation (i.e., across the surface perpendicular to the direction of rotation), thereby minimizing forces that tend to vary the trailing edge of the brake pad radially outward relative to its adjacent carrier mount abutment surfaces 27. Fig. 5 also shows the brake pad lateral projection receiving features 28 of this carrier mount embodiment that are complementarily shaped to receive the lateral projections 16 of the brake pad 10 to positively retain the brake pad within the disc brake.
The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since such modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and their equivalents.
List of reference markers:
1 disc brake
2 brake disc
3 brake caliper
4 Carrier mounting
5 clamp actuator mounting face
6 brake block
10 brake pad
11 brake pad backing plate
12,13 brake pad side surfaces
14 brake pad radial inner side
15 brake pad radially outward
16 lateral projection of back plate
17 radially outer retaining hook
18 radial outer plate wear sensor notch
19 brake pad friction material
20. Brake block
22,23 brake pad side surfaces
24 brake pad radial inner side
25 brake pad radially outward
26 Carrier mounting
27 Carrier mount brake pad abutment surface
28 Carrier Mount brake pad lateral protrusion receiving feature
101 brake disc
102 brake pad leading edge
103 brake pad trailing edge
Claims (10)
1. A disc brake, comprising:
a brake caliper;
a brake pad comprising a brake pad backing plate and a brake pad friction material affixed to the backing plate, an
A carrier mount having a brake pad abutment surface configured to receive the brake pad,
wherein,
the brake pad includes side surfaces generally aligned along a radius having a common origin substantially at the axis of rotation of the brake rotor,
the brake pad side includes a brake pad retaining feature protruding laterally from an underside of the brake pad,
the carrier mount brake pad abutment surface is configured to have a shape that complements a shape of the brake pad side surface and includes a receiving feature of a brake pad retaining feature,
the brake pad backing plate and brake pad friction material have an arc length in a circumferential direction of the brake disc that is greater on a radially outer region of the brake pad than on a radially inner region of the brake pad, and
the brake pad retaining feature cooperates with a receiving feature of the brake pad retaining feature of the carrier mount such that the brake pad is prevented from moving radially outward when in a mounted position in the brake.
2. The disc brake of claim 1,
the brake pad backing plate side surfaces and the brake pad friction material side surfaces have matching shapes.
3. The disc brake of claim 2,
each of the brake pad backing plate side surfaces is parallel to an adjacent one of the brake pad friction material side surfaces.
4. The disc brake of claim 1,
the side surfaces of the brake pad and the carrier mount brake pad abutment surfaces have complementary surface features configured to cooperate to retain the brake pad in the disc brake against radially outward movement during a braking operation.
5. The disc brake of claim 4,
the brake pad side surface features are lateral protrusions and the carrier mount brake pad abutment surface features are complementary lateral protrusion receiving recesses.
6. The disc brake of claim 1,
the arc length is approximately 5% of the outer circumference of the brake disc.
7. A brake pad, comprising:
a brake pad backing plate; and
a brake pad friction material affixed to the backing plate,
wherein,
the brake pad friction material includes side surfaces generally aligned along a radius having a common origin,
the brake pad friction material side surface and the brake pad backing plate side surface have matching shapes,
the brake pad side includes a brake pad retaining feature protruding laterally from an underside of the brake pad,
the brake pad backing plate side surface is configured to mate with a brake pad abutment surface of a carrier mount having a brake pad abutment surface that is generally aligned along a radius having an origin located approximately at the common origin when the brake pad is in a mounted position in the carrier mount, and
the brake pad retaining feature is configured to cooperate with a receiving feature of the brake pad retaining feature of the carrier mount such that the brake pad is prevented from moving radially outward when in a mounted position in the brake.
8. The brake pad of claim 7,
each brake pad friction material side is parallel to an adjacent one of the carrier mount abutment surfaces when in a mounted position in the carrier mount.
9. The brake pad of claim 7,
the lateral sides of the brake pad have brake pad surface features configured such that when in an installed position, the brake pad surface features cooperate with complementary surface features of the carrier mount to retain the brake pad in the disc brake against radially outward movement during a braking operation.
10. Brake pad according to claim 9,
the brake pad side surface features are lateral protrusions configured to engage complementary carrier mount brake pad abutment surface lateral protrusion receiving recesses.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US14/844,813 US9605721B1 (en) | 2015-09-03 | 2015-09-03 | Wear optimized pad design |
| US14/844,813 | 2015-09-03 | ||
| PCT/US2016/049872 WO2017040765A1 (en) | 2015-09-03 | 2016-09-01 | Wear optimized pad design |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108138877A CN108138877A (en) | 2018-06-08 |
| CN108138877B true CN108138877B (en) | 2020-07-07 |
Family
ID=58188332
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680055433.4A Active CN108138877B (en) | 2015-09-03 | 2016-09-01 | Wear optimized blade design |
Country Status (7)
| Country | Link |
|---|---|
| US (2) | US9605721B1 (en) |
| EP (1) | EP3344893A4 (en) |
| CN (1) | CN108138877B (en) |
| AU (1) | AU2016317850B2 (en) |
| CA (1) | CA2997351A1 (en) |
| RU (1) | RU2728201C2 (en) |
| WO (1) | WO2017040765A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9726243B2 (en) * | 2015-03-20 | 2017-08-08 | Bendix Spicer Foundation Brake Llc | Disc brake pad retention system and mounting method |
| US9605721B1 (en) * | 2015-09-03 | 2017-03-28 | Bendix Spicer Foundation Brake Llc | Wear optimized pad design |
| US9976610B2 (en) * | 2015-09-03 | 2018-05-22 | Bendix Spicer Foundation Brake Llc | Wear optimized pad design |
| WO2018148415A1 (en) | 2017-02-08 | 2018-08-16 | Bendix Spicer Foundation Brake Llc | Wear optimized pad design |
| CN108895096B (en) * | 2018-08-02 | 2019-12-03 | 江苏大学 | A kind of permanent magnetism double disk brake and its braking method |
| DE102018219752A1 (en) | 2018-11-19 | 2020-05-20 | Mando Corporation | Brake assembly |
| WO2024036415A1 (en) * | 2022-08-19 | 2024-02-22 | Nucap Industries Inc. | Reduced profile brake backing plate |
| CN119393469B (en) * | 2025-01-03 | 2025-03-28 | 温州力邦企业有限公司 | Split brake caliper of automobile |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4915198A (en) * | 1986-09-03 | 1990-04-10 | Akebono Brake Industry Co., Ltd. | Friction pad support mechanism for disc brake |
| US5125482A (en) * | 1989-09-13 | 1992-06-30 | Akebono Brake Industry Co., Ltd. | Disc brake elastic pressing members having unequal pressing forces |
| US6386335B1 (en) * | 2000-06-28 | 2002-05-14 | Kelsey-Hayes Company | Anchor bracket and brake shoe assembly for use in a disc brake assembly |
| CN101427044A (en) * | 2006-04-20 | 2009-05-06 | 大陆-特韦斯贸易合伙股份公司及两合公司 | Disk brake |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2926757A (en) * | 1956-05-11 | 1960-03-01 | Goodyear Tire & Rubber | Disc brake |
| US3990545A (en) | 1971-08-03 | 1976-11-09 | Daimler-Benz Aktiengesellschaft | Disk brake with floating saddle for vehicles |
| US4394891A (en) | 1980-01-19 | 1983-07-26 | Tokico Ltd. | Disc brake |
| CA2057983A1 (en) * | 1990-12-26 | 1992-06-27 | Rick D. Pelfrey | Disc brake assembly and brake pad for use therewith |
| DK0776429T3 (en) * | 1994-08-26 | 2002-10-07 | Brake Technologies Pty Ltd | Wet disc brake |
| DE4430955A1 (en) * | 1994-08-31 | 1996-03-07 | Teves Gmbh Alfred | Disc brake pad design |
| DE102004021126A1 (en) | 2004-04-29 | 2005-11-17 | Lucas Automotive Gmbh | disc brake |
| US7578374B2 (en) | 2005-07-19 | 2009-08-25 | Advics Co., Ltd. | Disk brake device |
| US8505699B2 (en) * | 2008-02-06 | 2013-08-13 | Material Sciences Corporation | Flanged shim for disc brake squeal attenuation |
| DE102009006283B4 (en) * | 2009-01-27 | 2022-11-10 | Zf Active Safety Gmbh | braking system |
| KR20110034885A (en) * | 2009-09-29 | 2011-04-06 | 주식회사 만도 | Car Disc Brake |
| JP5797428B2 (en) * | 2010-04-23 | 2015-10-21 | 日清紡ブレーキ株式会社 | Disc brake pad |
| JP5847561B2 (en) * | 2011-11-29 | 2016-01-27 | 日立オートモティブシステムズ株式会社 | Disc brake |
| US9726243B2 (en) * | 2015-03-20 | 2017-08-08 | Bendix Spicer Foundation Brake Llc | Disc brake pad retention system and mounting method |
| US9605721B1 (en) * | 2015-09-03 | 2017-03-28 | Bendix Spicer Foundation Brake Llc | Wear optimized pad design |
-
2015
- 2015-09-03 US US14/844,813 patent/US9605721B1/en active Active
-
2016
- 2016-09-01 CN CN201680055433.4A patent/CN108138877B/en active Active
- 2016-09-01 CA CA2997351A patent/CA2997351A1/en active Pending
- 2016-09-01 EP EP16842972.8A patent/EP3344893A4/en not_active Withdrawn
- 2016-09-01 WO PCT/US2016/049872 patent/WO2017040765A1/en active Application Filing
- 2016-09-01 RU RU2018111688A patent/RU2728201C2/en active
- 2016-09-01 AU AU2016317850A patent/AU2016317850B2/en active Active
-
2017
- 2017-02-03 US US15/423,953 patent/US9897152B2/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4915198A (en) * | 1986-09-03 | 1990-04-10 | Akebono Brake Industry Co., Ltd. | Friction pad support mechanism for disc brake |
| US5125482A (en) * | 1989-09-13 | 1992-06-30 | Akebono Brake Industry Co., Ltd. | Disc brake elastic pressing members having unequal pressing forces |
| US6386335B1 (en) * | 2000-06-28 | 2002-05-14 | Kelsey-Hayes Company | Anchor bracket and brake shoe assembly for use in a disc brake assembly |
| CN101427044A (en) * | 2006-04-20 | 2009-05-06 | 大陆-特韦斯贸易合伙股份公司及两合公司 | Disk brake |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3344893A1 (en) | 2018-07-11 |
| US9605721B1 (en) | 2017-03-28 |
| RU2018111688A (en) | 2019-10-07 |
| EP3344893A4 (en) | 2019-04-10 |
| US20170146081A1 (en) | 2017-05-25 |
| CN108138877A (en) | 2018-06-08 |
| AU2016317850A1 (en) | 2018-03-29 |
| HK1250770A1 (en) | 2019-01-11 |
| WO2017040765A1 (en) | 2017-03-09 |
| US9897152B2 (en) | 2018-02-20 |
| RU2018111688A3 (en) | 2020-03-18 |
| CA2997351A1 (en) | 2017-03-09 |
| RU2728201C2 (en) | 2020-07-28 |
| US20170067520A1 (en) | 2017-03-09 |
| AU2016317850B2 (en) | 2020-04-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108138877B (en) | Wear optimized blade design | |
| US10119581B2 (en) | Disc brake | |
| US10962068B2 (en) | Disc brake for a utility vehicle, and brake pad set | |
| JP4698147B2 (en) | Disc brake assembly | |
| EP3899306B1 (en) | Assembly of at least two brake pads and at least one spring | |
| CN104583631A (en) | Disc brake pad mounting and retention system and method | |
| CN104583630A (en) | Disc brake pad mounting and retention system and method | |
| US9976610B2 (en) | Wear optimized pad design | |
| US7461725B2 (en) | Disk brake | |
| JP2001065613A (en) | Disc brake device and band elastic device therefor | |
| AU2018217707B2 (en) | Wear optimized pad design | |
| HK1250770B (en) | Wear optimized pad design | |
| US8079448B2 (en) | Axle shaft including an electromechanically or pneumatically actuated disc brake | |
| FI3374655T3 (en) | Disc brake and pad assembly | |
| WO2025094039A1 (en) | Band spring shaped to be arranged straddling a brake disc | |
| HK1232935B (en) | Disk brake, brake caliper and brake pad set for a disk brake | |
| HK1232935A1 (en) | Disk brake, brake caliper and brake pad set for a disk brake |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| REG | Reference to a national code |
Ref country code: HK Ref legal event code: DE Ref document number: 1250770 Country of ref document: HK |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |